Phase Change Assembly For A Linear Friction Welding System

ABSTRACT

A phase change assembly for a linear friction welding system includes a single input shaft and a single output shaft with respective first and second gears, and a carriage rotatably supporting a third gear operably connected to the first and second gear and one of a roller and a fourth gear operably connected to the first and second gear. A linear actuator is operably connected to the carriage. A first stop is configured to stop movement of the carriage by the linear actuator in a first direction to provide a first predetermined phase relationship between the input shaft and the output shaft, and a second stop is configured to stop movement of the carriage by the linear actuator in a second direction opposite the first direction to provide a second predetermined phase relationship between the input shaft and the output shaft.

This application is a divisional application of co-pending U.S.application Ser. No. 16/751,343, filed on Jan. 24, 2020 which is adivisional application of U.S. application Ser. No. 16/161,611, filed onOct. 16, 2018 which issued as U.S. Pat. No. 10,569,355 on Feb. 25, 2020,which is a divisional application of U.S. application Ser. No.14/820,806, filed on Aug. 7, 2015, which issued as U.S. Pat. No.10,099,313 on Oct. 16, 2018, the entirety of which are each incorporatedby reference herein.

FIELD

The present disclosure relates to linear friction welding.

BACKGROUND

Friction welding (FW) is a process of joining two components which maybe made from the same or different materials. The FW process typicallyinvolves pressing one of the two components against the other componentwith a large amount of force and rapidly moving one of the twocomponents with respect to the other component to generate friction atthe interface of the two components. The pressure and movement generatesufficient heat to cause the components to begin to plasticize. Once thetwo components are plasticized at the contact interface, the relativemovement of the two components is terminated and an increased force isapplied. As the components cool in this static condition, a weld isformed at the contact interface.

The weld obtained using FW is a solid state bond which is highlyrepeatable and easily verifiable. For example, the amount of materialdonated by each component to the formation of the weld, which isreferred to as “upset”, is well defined. Therefore, by carefullycontrolling the energy input into the FW system in the form of frictionand forging pressure, the measured upset of a welded assembly providesverification as to the nature of the weld obtained.

As discussed above, relative movement of the two components is acritical facet of FW. Different approaches have been developed toprovide the required relative movement. One widely used approach isrotational friction welding (RFW). RFW involves rotation of onecomponent about a weld axis. RFW provides many benefits and is thus afavored welding approach in various industries including aerospace andenergy industries.

RFW, however, does have some limitations. For example, in forming aweld, the interface between the two components must be evenly heated togenerate a uniform plasticity within each of the components throughoutthe weld interface. If one area becomes hotter than another area, thematerial in that hotter area will be softer, resulting in an incongruityin the formed weld. To provide consistent heat generation throughout thecomponent interface, the rotated component is necessarily uniformlyshaped about the axis of rotation, i.e., circular. Moreover, since theheat generated is a function of the relative speed between the twomaterials, more heat will be generated toward the periphery of therotated component since the relative speed at the periphery is higherthan the relative speed at the rotational axis.

In response to the limitations of RFW, linear friction welding (LFW) wasdeveloped. In LFW, the relative movement is modified from a rotationalmovement to a vibratory movement along a welding axis. By controllingthe amplitude and the frequency of the linear movement, the heatgenerated at the component interface can be controlled.

LFW thus allows for welding of a component that exhibits substantiallyuniform width. LFW, like RFW, is subject to various limitations. Onesuch limitation is that LFW exhibits non-uniform heating along thewelding axis due to the linear movement of the vibrated component. Forexample, when welding two components of identical length along thewelding axis, the two components are aligned in the desired as-weldedposition. Due to the nature of previous LFW systems, this locationcorresponds to the rearmost position of the component which is moved.The leading edge of the vibrated component is then moved beyond thecorresponding edge of the stationary component by a distance equal tothe amplitude of the vibration. Moreover, the trailing edge of thevibrated component exposes a portion of the stationary component as theleading edge of the vibrated component moves beyond the correspondingedge of the stationary component. Accordingly, the portion of thevibrating component that moves beyond the corresponding edge of thestationary component and the exposed portion of the stationary componentwill not be heated at the same rate as the remaining surfaces at thecomponent interface. Therefore, manufacturing process must take theincongruity of the welds into account such as by machining off a portionof the welded components at the leading edge and the trailing edge ofthe formed weld.

Moreover, in order to achieve the frequency and amplitude necessary torealize a weld, a LFW device must provide for rapid acceleration from adead stop. The moving component must then be completely stopped andreaccelerated in a reverse direction. As the size of the vibratedcomponent increases, the momentum that must be controlled becomesproblematic. Thus, traditional LFW devices incorporate massivecomponents which are very expensive.

A related limitation of LFW processes is that the relative motionbetween the two components must be terminated in order for the weld toform properly. Merely removing the motive force does not remove themomentum of the vibrated component. Additionally, any “rebound” ordamped vibrations of the moving component as it is immobilized weakensthe final weld since the plasticized metals begin to cool as soon as thevibrating movement is reduced.

One approach to solving the need to rapidly immobilize the movingcomponent is to jam the motion-inducing system such as by forciblyinserting a device into the motion inducing system. Freezing the systemin this fashion can provide the desired stopping time. This approach,however, results in significant forces being transmitted through thesystem, necessitating oversized components to be able to withstand theshock. Moreover, the exact position of the vibrated component withrespect to the stationary component is not known. Therefore,manufacturing processes must account for a possible position errorpotentially equal to the amplitude of vibration.

Therefore, a LFW system and method which provides consistent welds isbeneficial. A LFW system and method which allows for smaller componentswithin the system would be beneficial. A LFW system and method whichreduce the errors associated with the LFW process would be furtherbeneficial.

SUMMARY

The present disclosure in one embodiment provides a phase changeassembly for a linear friction welding system which includes a singleinput shaft and a single output shaft with respective first and secondgears, and a carriage rotatably supporting a third gear operablyconnected to the first and second gear and one of a roller and a fourthgear operably connected to the first and second gear. A linear actuatoris operably connected to the carriage. A first stop is configured tostop movement of the carriage by the linear actuator in a firstdirection to provide a first predetermined phase relationship betweenthe input shaft and the output shaft, and a second stop is configured tostop movement of the carriage by the linear actuator in a seconddirection opposite the first direction to provide a second predeterminedphase relationship between the input shaft and the output shaft.

In some embodiments, a linear friction welding system includes a ramconfigured to vibrate along a welding axis, a cam follower operablyconnected to the ram, an eccentric including an eccentric outerperiphery operably engaged with the cam follower, and an innerperiphery, a first power shaft slidingly engaged with the eccentric, asecond power shaft eccentrically engaged with the inner periphery, atiming component operably connected to the first power shaft and thesecond power shaft, a motor configured to drive the timing component,and a phase change mechanism engaged with the timing component andmovable between a first position defining a first phase relationshipbetween the first power shaft and the second power shaft, and a secondposition defining a second phase relationship between the first powershaft and the second power shaft.

In some embodiments, the timing component includes a timing componentload segment between the first power shaft and the second power shaft,the phase change mechanism defines a first timing component load segmentlength when the phase change mechanism is in the first position, thephase change mechanism defines a second timing component load segmentlength when the phase change mechanism is in the second position, andthe first timing component load segment length is greater than thesecond timing component load segment length.

In other embodiments, the timing component is operably connected to thefirst power shaft through a first gear, the timing component is operablyconnected to the second power shaft through a second gear, and the phasechange mechanism includes a third gear operably engaged with the timingcomponent.

In further embodiments, the third gear is operably engaged with thetiming component load segment, and the phase change mechanism includes afourth gear operably engaged with a feed segment of the timingcomponent.

In certain embodiments, the timing component is a timing belt.

In yet another embodiment, the phase change mechanism further includes acarriage rotatably supporting the third gear and the fourth gear, andthe carriage is movable by a linear actuator between the first positionand the second position.

In another embodiment of the system, the carriage is movable between thefirst position and the second position along a phase change axis, thephase change mechanism includes a transfer plate fixedly connected tothe carriage and to an actuator piston, the transfer plate is arrangedto contact a first stop when the carriage is in the first position, andthe transfer plate is arranged to contact a second stop when thecarriage is in the second position.

In additional embodiments of the system, the first stop is selectablypositionable at any one of a first plurality of locations so as tomodify the location of the first position along the phase change axis.

In other embodiments of the system, the second stop is selectablypositionable at any one of a second plurality of locations so as tomodify the location of the second position along the phase change axis.

In yet other embodiments, the first stop comprises a first threaded boltconfigured such that rotation of the first threaded bolt moves the firststop from a first of the first plurality locations to a second of thefirst plurality locations, and the second stop comprises a secondthreaded bolt configured such that rotation of the second threaded boltmoves the second stop from a first of the second plurality of locationsto a second of the second plurality of locations

Another embodiment is directed to a method of operating a linearfriction welding system that includes (i) a ram configured to vibratealong a welding axis, (ii) a cam follower operably connected to the ram,(iii) an eccentric including an eccentric outer periphery operablyengaged with the cam follower, and an inner periphery, (iv) a firstpower shaft slidingly engaged with the eccentric, (v) a second powershaft eccentrically engaged with the inner periphery, (vi) a firsttiming component configured to drive both the second power shaft and aphase change assembly drive shaft, (vii) a motor configured to drive thefirst timing component, and (viii) a phase change assembly driven by thephase change assembly drive shaft.

The method includes positioning the phase change assembly in a firstconfiguration thereby establishing a phase relationship between thefirst power shaft and the second power shaft whereat the ram does notvibrate when the first power shaft and the second power shaft rotate,and driving the timing component with the motor. Driving the motorresults in driving the first power shaft and the phase change assemblywith the timing component with the phase change assembly in the firstconfiguration and driving the driving the second power shaft with thephase change assembly while the phase change assembly is in the firstconfiguration. A establishing a scrub pressure is then establishedbetween two components to be welded with the phase change assembly inthe first configuration while the first timing component is beingdriven.

When the scrub pressure is applied, a second phase relationship betweenthe first power shaft and the second power shaft is established bymoving the phase change assembly to a second configuration while thefirst power shaft and the second power shaft are being driven, therebycausing the ram to vibrate along the welding axis.

When the scrub is complete, the first phase relationship between thefirst power shaft and the second power shaft is reestablished byreturning the phase change assembly from the second configuration to thefirst configuration resulting in stoppage of movement between thecomponents. A forge pressure is then established between the twocomponents with the phase change assembly returned to the firstconfiguration.

In one or more embodiments, moving the phase change assembly to thesecond configuration includes lengthening a load segment of a secondtiming component of the phase change assembly.

In one or more embodiments, lengthening the load segment includes movinga carriage rotatably supporting a gear engaged with the second timingcomponent load segment along a phase change axis.

In one or more embodiments moving the carriage includes moving thecarriage from a first location associated with the first configurationtoward a second location associated with the second configuration with alinear actuator.

In one or more embodiments moving the phase change assembly to thesecond configuration includes stopping movement of the carriage towardthe second location with a first stop.

In one or more embodiments, a method includes determining a desired ramvibration amplitude and setting a position of the first stop based uponthe desired ram vibration amplitude.

In one or more embodiments returning the phase change assembly includesmoving the carriage toward the first location with the linear actuator,and stopping movement of the carriage toward the first location with asecond stop.

In one or more embodiments positioning the phase change assembly at thefirst location includes positioning the second stop at a locationwhereat when the carriage contacts the second stop the ram does notvibrate when the first power shaft and the second power shaft rotate.

In one or more embodiments setting the position of the first stopincludes changing the location of the first stop by rotating a firstthreaded bolt.

In one or more embodiments positioning the second stop includes changingthe location of the second stop by rotating a second threaded bolt.

The above described features and advantages, as well as others, willbecome more readily apparent to those of ordinary skill in the art byreference to the following detailed description and accompanyingdrawings.

BRIEF DESCRIPTION OF THE DRAWINGS

The present disclosure may take form in various system and methodcomponents and arrangement of system and method components. The drawingsare only for purposes of illustrating exemplary embodiments and are notto be construed as limiting the disclosure.

FIG. 1 depicts a partial side plan view of a linear friction weldingsystem in accordance with principles of the disclosure;

FIG. 2 depicts a partial front cross-sectional view of the system ofFIG. 1;

FIG. 3 depicts a top cross-sectional view of the vibrating system of thelinear friction welding system of FIG. 1 depicting an eccentric portionof an inner power shaft positioned within an eccentric, with aneccentric outer surface and an outer power shaft engaged with theeccentric;

FIG. 4 depicts a front cross-sectional view of the vibrating system ofFIG. 3;

FIG. 5 depicts a rear plan view of the motor, vibrating system and phasechange assembly of FIG. 1;

FIG. 6 depicts a perspective view of the interior of the phase changeassembly of FIG. 5;

FIG. 7 depicts a plan view of the interior of the phase change assemblyof FIG. 6 with the phase change mechanism in a first position;

FIG. 8 depicts a perspective view of the phase change mechanism of thephase change assembly depicted in FIG. 7;

FIG. 9 depicts partial perspective view of the phase change assembly ofFIG. 5 depicting the linear actuator and the phase change mechanism;

FIG. 10 depicts a schematic view of the control system of the linearfriction welding system of FIG. 1;

FIG. 11 depicts a simplified plan view of the phase change assembly ofFIG. 5 with the phase change mechanism in a first position;

FIG. 12 depicts a simplified plan view of the phase change assembly ofFIG. 5 with the phase change mechanism in a second position; and

FIG. 13 depicts a procedure that can be executed under the control ofthe control system of FIG. 10 to form a welded unit with the linearfriction welding system of FIG. 1;

DETAILED DESCRIPTION

Referring to FIG. 1, a linear friction welding system 100 includes apressing assembly 102 and a vibrating assembly 104 positioned within aframe 106. The pressing assembly 102 includes an upper assembly 108 anda lower assembly 110. The upper assembly includes a base 112, and tworocker arm pairs 114 and 116 supporting a carriage 118 as further shownin FIG. 2.

Continuing with FIG. 2, the lower assembly 110 is generally aligned withthe carriage 118 and includes a forge platen 120 supported above a mainhydraulic press 122. The main hydraulic press 122 defines a press axis124. An anti-rotation rod 126 extends from the forge platen 120 througha lower support plate 128. A sensor 130 is associated with theanti-rotation rod 126. In one embodiment, the sensor 130 is a linearvoltage displacement transducer (LVDT).

Returning to FIG. 1, the vibrating assembly 104 includes a motor 140, aphase change assembly 142, a cam assembly 144, and a ram 146. The ram146 is pivotably connected to the carriage 118 at a forward end and ispivotably connected to the cam assembly 144 at the opposite end througha connecting rod 148. The ram 146 is configured for movement along aweld axis 150. The motor 140 is connected to the cam assembly 144 andthe phase change assembly 142 through a belt 152. A belt tensioner 154is provided for the belt 152 which is driven by a geared shaft 158 ofthe motor 140.

The cam assembly 144, shown in more detail in FIGS. 3-4, includes aninner power shaft 160, an outer power shaft 162, a coupler 164, aneccentric 166, and a cam follower 168. The inner power shaft 160, whichin one embodiment is a “second power shaft”, is operably coupled withthe motor 140 through the belt 152 and a gear 156 (see FIG. 1) androtates about an axis of rotation 170. The inner power shaft 160includes an eccentric portion 172 and a projection 174. The outer powershaft 162, which in one embodiment is a “first power shaft”, is operablycoupled with the motor 140 through the belt 152 and the phase changeassembly 142, as discussed in further detail below, and also rotatesabout the axis of rotation 170. The outer power shaft 162 includes acavity 176 configured to rotatably receive the projection 174. Rotatableengagement of the projection 174 within the cavity 176 keeps both theinner and outer power shafts 160/162 coaxial with the axis of rotation170.

The coupler 164 is a modified Oldham coupler including one bifurcatedtongue 178 which mates with a groove 180 in the outer power shaft 162(see FIG. 3) and a second bifurcated tongue 182, rotated ninety degreeswith respect to the bifurcated tongue 178, which mates with a groove 184in the eccentric 166 (see FIG. 4). The eccentric 166 further includes anouter eccentric periphery 186 and an inner periphery 188 defining athrough-bore 190. The bore 190 is sized to rotationally receive theeccentric portion 172 of the inner power shaft 160. The outer eccentricperiphery 186 defines a diameter that is closely fit within the innerdiameter of the cam follower 168.

The connecting rod 148 of the cam assembly 144 is pivotably connected tothe ram 146 through a pivot 192 (see FIG. 1). The ram 146 is in turnpivotably connected to the carriage 118 through a lower pivot pair 194(only one is shown). The lower pivot pair 194 also pivotably connectsthe carriage 118 with a rearward rocker arm of each of the rocker armpairs 114 and 116. Another lower pivot pair 196 shown in FIGS. 1 and 2pivotably connects the carriage 118 with a forward rocker arm of each ofthe rocker arm pairs 114 and 116. Four pivots 198 pivotably connect eachof the rocker arms in the rocker arm pairs 114 and 116 to the base 112.

As noted above, the outer power shaft 162 is operably coupled with themotor 140 through the phase change assembly 142. The indirect couplingis described with initial reference to FIG. 5 which shows the belt 152configured to drive a phase change assembly shaft 210 through a gear212. The shaft 210 drives the outer power shaft 162 through the phasechange assembly 142 which is depicted in FIG. 6 with its front wallremoved.

The phase change assembly 142 includes a gear 214, which in oneembodiment is a first gear, connected to the shaft 210. A timing belt216 (which in one embodiment is a “second timing component”) operablyconnects the gear 214 with a gear 218, which in one embodiment is asecond gear, which is operably connected to the shaft 162. The belt 216is engaged with four tensioners 220, 222, 224, and 226, and a phasechange mechanism 228.

The phase change mechanism 228 is further depicted in FIGS. 7 and 8 andincludes a carriage 230 which rotatably supports two gears 232 (which inone embodiment is a “fourth gear”) and 234 (which in one embodiment is a“third gear”), although in some embodiments a roller is used in place ofone of the gears 232 and 234. The carriage 230 is slidably supportedwithin the phase change assembly 142 on one side by rail 236 whichslides within guides 238 and 240 (FIG. 7) and on the other side by rail242 which slides within guides 244 and 246 (FIG. 8). A transfer plate248 is mounted to, or formed integrally with, the rear side of thecarriage 230.

As shown in FIG. 9, the transfer plate 248 is fixedly connected to apiston 260 of a linear actuator assembly 262. The linear actuatorassembly 262 is mounted to the phase change assembly 142 and oriented tomove the carriage 230 along a linear actuator axis 264. The linearactuator assembly 262 is controllable between a first condition which,in the depiction of FIG. 9, urges the piston 260 rightwardly untilmovement is terminated by a first stop 266, and a second conditionwhich, in the depiction of FIG. 9, urges the piston 260 leftwardly untilmovement is terminated by a second stop 268. The second stop 268 in thisembodiment is a bolt threadedly engaged with a stop mount 270 and thefirst stop 266 is a bolt threadedly engaged with the linear actuatorassembly 262.

The linear friction welding system 100 also includes a welding controlsystem 280 depicted in FIG. 10. The control system 280 includes an I/Odevice 282, a processing circuit 284 and a memory 286. The controlsystem 280 is operably connected to the main hydraulic press 122, themotor 140, the linear actuator assembly 262, and a sensor suite 288. Insome embodiments, one or more of the components of the system 280 areprovided as a separate device which may be remotely located from theother components of the system 280.

The I/O device 282 in some embodiments includes a user interface,graphical user interface, keyboards, pointing devices, remote and/orlocal communication links, displays, and other devices that allowexternally generated information to be provided to the control system280, and that allow internal information of the control system 280 to becommunicated externally.

The processing circuit 284 may suitably be a general purpose computerprocessing circuit such as a microprocessor and its associatedcircuitry. The processing circuit 284 is operable to carry out theoperations attributed to it herein.

Within the memory 286 are various program instructions 290. The programinstructions 290, some of which are described more fully below, areexecutable by the processing circuit 284 and/or any other components ofthe control system 280 as appropriate. Parameter databases 292 are alsolocated within the memory 286.

Many components in the above described linear friction welding system100 are similar to, and work in like manner as, components in the systemdescribed in detail in U.S. Pat. No. 8,376,210, incorporated herein byreference. By way of example, when the inner power shaft 160 has thesame relative rotational position as the outer power shaft 162, therelative phase of the inner power shaft 160 and the outer power shaft162 are said to be matched, which may alternatively be referred to asbeing in phase, having the same relative phase, or having a system phaseangle of zero. With a system phase angle of zero, and with the motor 140operating, the ram 146 remains motionless. Movement of the ram 146 alongthe weld axis 150 is effected by controlling the shafts 160 and 162 toestablish a non-zero phase angle.

The linear friction welding system 100 differs from the system disclosedin the '210 patent, however, in the manner in which the system phaseangle is established while using a single motor. This difference isrealized by the incorporation of the phase change assembly 142.Specifically, the belt 152 in one embodiment is a first timing componentwhich rotates the gear 154 and the gear 212 at a fixed phaserelationship. While there is a fixed relationship between the gear 154and the inner power shaft 160, the relationship between the gear 212 andthe outer power shaft 162 is variable because of the phase changeassembly 142 as discussed with further reference to FIGS. 11 and 12.

In FIG. 11, the linear actuator assembly 262 has been controlled todrive the transfer plate 248 against the stop 266 (FIG. 9), and theposition of the stop 266 has been adjusted by selective threading of thestop 266 into the linear actuator assembly 262 to provide a zero systemphase angle. In the condition of FIG. 11, the timing belt 216 is definedby a feed segment 300 and a timing component load segment 302. The feedsegment 300 is defined as the portion of the timing belt 216 between thegears 214 and 218 from point 304 at the top of the gear 214 extendingalong the gear 232 to point 306 at the bottom of the gear 218. The loadsegment 302 is defined as the portion of the timing belt 216 between thegears 214 and 218 from point 304 at the top of the gear 214 extendingalong the gear 234 to point 306 at the bottom of the gear 218.

By controlling the phase change mechanism 228 to drive the transferplate 248 against the stop 268 (FIG. 9), the carriage 230 is driven inthe direction of the arrow 308 in FIG. 11 to the position depicted inFIG. 12. In FIG. 12, the length of the load segment 302′ of the timingbelt 216 is greater than the length of the load segment 300 in FIG. 11.Because both of the gears 214 and 218 are engaged with the belt 216, thebelt 216 cannot simply slide past the gears 214 and 218. Rather, atleast one of the gears 214/218 must rotate in order to allow for some ofthe belt 216 on the feed segment 300 to move over to the load segment302′.

Rotation of the gear 214, however, is effected by the motor 140 throughthe belt 152 (see FIG. 1). Accordingly, movement of the carriage 230forces the gear 218 to rotate to allow a portion of the belt 216 totransfer from the feed side 300 to the load side 302′. This is indicatedin FIGS. 11 and 12 by schematic marks 310 and 312. As evidenced bycomparing the mark 310 in FIG. 11 with the mark 310′ in FIG. 12, therotational position of the gear 214 does not change as the carriage 230moves. The mark 312′ in FIG. 12, however, indicates that the gear 218has rotated from the location of the gear 218 in FIG. 11 as indicated bythe mark 312.

Accordingly, since the shafts 160 and 162 were in phase when the phasechange mechanism 228 was in the condition of FIG. 11, the shafts 160 and162 are out of phase when the phase change mechanism 228 is in thecondition of FIG. 12. While the gear 214 was not rotating in theforegoing explanation, those of skill in the art will recognize that thesame discussion applies when the gear 214 is rotating. Thus, it is therelative speed of the gear 218 which is momentarily modified by movementof the carriage 230. Consequently, with the motor 140 running, the ram146 will vibrate along the welding axis 150 as discussed in more detailin the '210 patent once the carriage moves away from the location ofFIG. 11.

In order to stop vibration of the ram 146, the carriage is simplycontrolled back to the position of FIG. 11, resulting in a momentaryslowing of the rotation of the gear 214 forcing the shaft 162 back intophase with the shaft 160. In one embodiment, the linear actuatorassembly 262 is configured to selectively direct hydraulic fluid to oneside or the other of a disk connected to the piston 260 and within thecylinder of the linear actuator assembly. Accordingly, the carriage israpidly forced between the positions of FIGS. 11 and 12, and maintainedat the desired position with continued hydraulic pressure against thedisk to ensure the phasing of the shafts 160/162 does not inadvertentlyshift.

Additional details of the linear friction welding system 100 areprovided with reference to a method 320 in FIG. 13, portions of whichare performed under the control the control system 280. At block 322,the system phase angle is set to zero with the transfer plate 248controlled against the stop 266. While a zero system phase angle can beestablished with the motor 140 de-energized, in one embodiment the motor140 is energized, and the bolt 266 is rotated until there is no movementof the ram 146.

At block 324 the amplitude for movement of the ram 146 is set. Becausethere is a fixed relationship between the phasing of the shafts 160/162and the amplitude of vibration of the ram 146, the distance between thetransfer plate 248 and the stop 268 establishes the amplitude ofvibration. In one embodiment, a chart is provided which identifies thespatial relationship needed for a desired amplitude. The amplitude isthen established by rotation of the stop 268 to the distance associatedwith the desired amplitude.

One of the components to be welded is then mounted to the forge platen120 and the other component is mounted to the carriage 118 (block 326).Control of the method 320 is then passed to the control system 280. Atblock 328 the processing circuit 284 executes program instructions 290to establish a scrub pressure between the components to be welded. Theprocessing circuit then controls motor 140 to the desired speedassociated with the scrub (in some systems only a single speed isavailable) and controls the linear actuator assembly 262 to drive thetransfer plate 248 against the stop 266 to initiate oscillation of theram 146 and perform a scrub (block 330). The scrub pressure and scrubfrequency in some embodiments are parameters stored in the parameterdatabases 292.

Once the scrub pressure, scrub frequency, and scrub amplitude have beenestablished, a scrub timer is started and counted down using a systemclock or other appropriate clock. As the scrub is performed, a “wipingaction” is generated by the linear friction welding system 100 asdiscussed more fully in the '210 patent.

When the desired scrub has been performed at block 330, burn parametersare established in the linear friction welding system 100 at block 332.Specifically, the processing circuit 284 controls the main hydraulicpress 122 to achieve a desired burn pressure based upon a value storedin the parameters database 292. The processing circuit 284 furtherobtains a burn frequency from the parameters database 292 and controlsthe speed of the motor 140 to a speed corresponding to the desired burnfrequency. In one embodiment, all of the changes from the scrubparameters to the burn parameters are controlled to occur substantiallysimultaneously.

Once the burn pressure and burn frequency, have been established, a burntimer is started and counted down using a system clock or otherappropriate clock. During the burn, the processing circuit 284 obtainsinput from the sensor suite 288 and modifies the speed of the motor 140as needed to maintain the desired burn frequency and controls the mainhydraulic press 122 to maintain the desired burn pressure.

When the burn timer has expired, movement of the ram 146 is terminatedat block 334. Movement can be terminated under the control of theprocessing circuit 284 by controlling the linear actuator 262 to movethe phase change mechanism 228 from the second position (FIG. 12) backto the first position (FIG. 11) whereby the relative phase of the innerand outer shafts 160/162 are again matched. The transfer plate 248 isthus forced into contact with the stop 266.

While the motor 140 rotates with no movement of the ram 146, theprocessing circuit 284 controls the main hydraulic press 122 toestablish a forge pressure at block 336 between the two weld componentsbased upon data stored in the parameters database 292. The forgepressure applied to properly burned components which are not moving withrespect to one another welds the two components together into a weldedunit.

Once the components have been welded, the welded unit is removed (block338) and the weld verified (block 340). If desired, the processingcircuit 284 may be used to determine the weld quality. Specifically, theinitial position of the forge platen 120 as the two weld components cameinto contact can be stored and compared to the position of the forgeplaten 120 after a weld has been formed. The difference between the twolocations indicates a loss of material from the two components at thecontact point of the two components.

Additionally, the temperature of the two components can be established,either by sensory input from the sensor suite 288 and/or by historicknowledge of the effects of the scrub and burn processes on thematerials of the two components. Furthermore, the actual pressure,frequency, and amplitude of the procedure 320 provide preciseinformation about the amount of energy placed into the components duringthe procedure 320. Consequently, the foregoing data may be used tocalculate the amount of material lost due to flash and the nature of theweld formed.

The linear welding system 100 thus provides precise and independentcontrol of pressure applied as well as the frequency and amplitude ofoscillation during the procedure 320. The use of a phase change assembly142 reduces the number of motors required for operation from othermethods. In addition, the phase change assembly 142 allows for the motorto remain on in between welds without movement of the ram.

While the present disclosure has been illustrated by the description ofexemplary processes and system components, and while the variousprocesses and components have been described in considerable detail, theapplicant does not intend to restrict or in any limit the scope of theappended claims to such detail. Additional advantages and modificationswill also readily appear to those skilled in the art. The disclosure inits broadest aspects is therefore not limited to the specific details,implementations, or illustrative examples shown and described.Accordingly, departures may be made from such details without departingfrom the spirit or scope of applicant's general inventive concept.

The claimed invention is:
 1. A phase change assembly for a linearfriction welding system, comprising: a sole input shaft defining a firstfixed axis; a first gear mounted to the sole input shaft; a sole outputshaft defining a second fixed axis; a second gear mounted to the soleoutput shaft; a carriage rotatably supporting a third gear operablyconnected to the first and second gear, and rotatably supporting one ofa roller and a fourth gear, the one of the roller and the fourth gearoperably connected to the first and second gear; a linear actuatoroperably connected to the carriage; a first stop configured to stopmovement of the carriage by the linear actuator in a first direction toprovide a first predetermined phase relationship between the sole inputshaft and the sole output shaft; and a second stop configured to stopmovement of the carriage by the linear actuator in a second directionopposite the first direction to provide a second predetermined phaserelationship between the sole input shaft and the sole output shaft. 2.The phase change assembly of claim 1, wherein the linear actuator isoperably connected to the carriage by a transfer plate extending fromthe carriage and coupled to a piston of the linear actuator.
 3. Thephase change assembly of claim 2, wherein the first stop comprises abolt threadedly engaged with the transfer plate.
 4. The phase changeassembly of claim 3, wherein the second stop comprises a bolt threadedlyconnected to a fixed support structure of the phase change assembly andaligned with the transfer plate.
 5. The phase change assembly of claim4, wherein the linear actuator is a hydraulic fluid linear actuator. 6.The phase change assembly of claim 2, wherein: the carriage is locatedbetween the first gear and the second gear.
 7. The phase change assemblyof claim 1, further comprising: a timing component operably connected tothe first gear, the second gear, the third gear, and the one of theroller and the fourth gear.
 8. The phase change assembly of claim 7wherein the one of the roller and the fourth gear is the fourth gear. 9.The phase change assembly of claim 7, wherein the timing component is atiming belt.